Process for straightening elongate members

ABSTRACT

The disclosure is directed to a straightening device for elongate elements such as shafts, rods, bars, tubes and the like and a process for straightening such members in which a member to be straightened is subjected to a progressive eccentric and oscillating force in relation to a point or points establishing an ultimate true center position, the resulting oscillating movement and displacement of the elongate member being such as to exceed the yield point of the material thereof and then returns the elongate member to a true axial position as established between the fixed true centers. The processes also comtemplate straightening to plural axes simultaneously. A trace of the movement of the shaft, for example, describes an increasing progressive spiral outward and a following decreasing regressive inward spiral return to the true center. The machine provides a variably eccentric spindle which is progressively movable from zero eccentricity during continuous rotation to a maximum eccentricity sufficient to deform the stock beyond the yield point thereof and the compound consequence of rotation with eccentric displacement is an oscillation imparted to the elongate members by a member encircling pitman or arm. In this action the workpiece is rotated or oscillated at least once after its yield point is exceeded before regressive eccentricity gradually returns the workpiece to a zero deflection position. Both rotational movement and eccentric control are transmitted to twinned adjacent spindles so as to accommodate plural shafts in the same action and the pitman arm is common to both spindles. The disclosure is also directed to the transfer aspects of the shafting for insertion and removal. The disclosure is also directed to such devices paired in face to face synchronized motion admitting of plural applications of eccentric and rotating force to parallel shafts as required.

[ Feb. 20, 1973 [54] PROCESS FOR STRAIGHTENING ELONGATE MEMBERS [75] Inventors: Edward E. Judge, Sr.; Edward E.

Judge, Jr., both of Lansing, Mich.

[73] Assignee: Industrial Metal Products Corporation, Lansing, Mich.

22 Filed: Oct. 15, 1968 211 Appl. No.: 767,605

[52] US. Cl ..72/389, 72/297 [51] Int. Cl. ..B2ld 9/05 [58] Field of Search....72/73, 74, 102, 112, 293, 296,

Primary Examiner-Charles W. Lanham Assistant ExaminerMichael J. Keenan Attorney-Miller, Morriss, Pappas & McLeod [57] ABSTRACT The disclosure is directed to a straightening device for elongate elements such as shafts, rods, bars, tubes and the like and a process for straightening such members in which a member to be straightened is subjected to a progressive eccentric and oscillating force in relation to a point or points establishing an ultimate true center position, the resulting oscillating movement and displacement of the elongate member being such as to exceed the yield point of the material thereof and then returns the elongate member to a true axial position as established between the fixed true centers. The processes also comtemplate straightening to plural axes simultaneously. A trace of the movement of.

the shaft, for example, describes an increasing progressive spiral outward and a following decreasing regressive inward spiral return to the true center. The machine provides a variably eccentric spindle which is progressively movable from zero eccentricity during continuous rotation to a maximum eccentricity sufficient to deform the stock beyond the yield point thereof and the compound consequence of rotation with eccentric displacement is an oscillation imparted to the elongate members by a member encircling pitman or arm. in this action the workpiece is rotated or oscillated at least once after its yield point is exceeded before regressive eccentricity gradually returns the workpiece to a zero deflection position. Both rotational movement and eccentric control are transmitted to twinned adjacent spindles so as to accommodate plural shafts in the same action and the pitman arm is common to both spindles. The disclosure is also directed to the transfer aspects of the shafting for insertion and removal. The disclosure is also directed to such devices paired in face to face synchronized motion admitting of plural applications of eccentric and rotating force to parallel shafts as required.

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SHEET 8 OF 6 m0 ma INVENTORS @wzaidwzaz.

ATTORNEYS PROCESS FOR STRAIGHTENING ELONGATE MEMBERS The present invention is directed to a new and improved shaft straightener in which a plurality of shafts are simultaneously acted upon by a pair of coordinated spindles at selectively progressive eccentricity during rotation and wherein the coordinated motion of the spindles is transmitted through a pitman or arm encircling the elongate member or shaft stock. The coordination of spindle eccentricity and rotation causes the elongate elements to flex beyond the yield point in a progressive outward spiral and at least one re olution beyond the yield point is preferably accomplished with subsequent regressive spiral return to center. Hence, shafts and the like are straightened by the process and machine as between at least three points, one of which is movable. The machine and process also allows axial loading and transfer of successive workpieces. The invention also is directed to the novel process of shaft straightening as embodied in the machine and which may contemplate the adoption of other machines once the process is fully comprehended.

The closest reference art known to the applicants is our U.S. Pat. No. 2,827,943 in which we employ a vane type hydraulic motor to actuate an eccentric to impart straightening force to shafts and the like. In addition, the U.S. Pat. to Bohm No. 3,176,496 and Schmitt No. 3,254,520 indicate the use of movable pass-through tooling oscillated from a pair of separate crank arms to act upon stock moving or drawn through the tooling. This concept as expressed in the Bohm and Schmitt work appears to be an extension of the wire straightening art in which stock is drawn or forced through a deforming station in removal of kinks before coiling. We believe that our method and apparatus are distinguishable over this known art.

The principal object of the present invention is to provide a machine for straightening shafts in which the straightening is accomplished by coordinated eccentric displacement and simultaneous oscillating or rotational displacement by rotation of a common spindle.

Another principal object of the present invention is to mechanically synchronize the movement in one spindle with an adjacent parallel spindle both as to rotation and selected variable eccentricity.

Another object is to provide a shaft straightening machine in which the loading and unloading of the machine can be accomplished axially and a pitman common to both spindles transmits changing oscillation and displacing motion to a plurality of workpieces.

Another object is to provide a method and machine for stress relieving shafts and other elongate objects such as crankshafts where plural parallel axes are included.

Still another object is to provide a compact structure and simple process whereby a maximum power input is made possible by small incremental application of deflecting force to a workpiece through plural revolutions of the spindle with attendant economies. In the drawings:

FIG. 1 is a top plan view of a straightening machine for shafts embodying the present invention.

FIG. 2 is a front elevation view of the machine as viewed in FIG. 1.

FIG. 3 is a side elevation view of the operating spindle of the present invention from the worm drive side.

FIG. 4 is a partial section view taken on the line IV-- IV of FIG. 1 and illustrating the journalled pair of spindles mechanically synchronized.

FIG. 5 is a section view taken on the line V--V of FIG. 2 and indicating the worm drive and orientation of the eccentric spindles in the spindle housing.

FIG. 6 is an end elevation view of the spindle housing and indicating tooling receivers or shaft supports mounted on the top of the housing in the ways and tool slide and in phantom line indicating additional tooling for simultaneous handling of additional elongate workpieces. (VI--VI FIG. 2.)

FIG. 7 is an end elevation view of the oscillating crank arm or pitman plate as secured to the spindles and extending upwardly to surround the shafts or elongate members to be straightened and thereby transposing the action of the spindles to the workpieces.

FIG. 8 is a full section view take of the line VIII VIII of FIG. 7 and revealing the construction of the crank or pitman arm which translates the coordinated motion of the spindles to the shafts or elongate members.

FIG. 9 is a top plan view of the pitman arm secured to both spindles.

FIG. 10 is an end elevation view of the shaft receivers in enlarged form and through which the shafts or elongate members are extended.

FIG. 11 is a side elevation view of the shaft receivers seen in FIG. 10 and indicating fasteners for selected positioning in T-slots in the guideways and the like.

FIG. 12 is a section view taken on the line XII--Xll of FIG. 10 and illuminating the universal self aligning character of the receiver construction to maintain alignment of the center of the elongate member while accomodating axial repositioning about the fixed center.

FIG. 13 is a front elevation schematic view of a straightener in accord with the present invention in which spaced apart connected spindles are utilized in synchronous manner to provide plural points of application of eccentric and rotational movement to an elongate element to be straightened.

FIG. 14 is a schematic side elevation view of a bar, rod or shaft undergoing straightening and indicating the trace of deflection in the shafts in hidden edge line.

FIG. 15 is a schematic end elevation of the pitman or crank arm surrounding the shaft to be straightened and illustrating the generation of lineal movement in phantom line as imparted to arm and shaft to be straightened.

FIG. 16 is a schematic end elevation of the shaft to be straightened and indicating the progressive deflection of the shaft rod or bar while rotating and the progressive return to center. The maximum deflection is beyond the yield point of the stock. The center point of the stock at completion is returned to the axis established by the movable tooling at zero deflection with the spindles still rotating and concurrently the fixed tooling establishes finish control points which may or may not be on the same finish axis as the movable tooling fixture.

GENERAL DESCRIPTION The process for straightening elongate elements such as rods, bars, tubes or shafts in accord with the present invention includes progressively deflecting or displacing the elongate shaft, tube or bar or rod at a selected point while rotating or oscillating the shaft or rod and wherein the maximum deflection causes the material to exceed the yield point for the material and then regressively returning the elongate shaft, tube, bar or rod while rotating to a true center of zero displacement. At least one and preferably several revolutions of the stock should occur at maximum deflection and beyond the yield point before the regressive return to new displacement. A true axis is maintained by providing two center positions which remain fixed and the oscillational deflection occurs intermediate the fixed tooling. To accomplish this the centers are spherically or universally socketed so that the axial displacement can occur but always passing through the fixed center points as selectively located by the tooling. The result is I a thorough strain relieving of the shaft, tube, rod or bar and an establishment of a true alignment relationship. To the extent that axial displacement occurs on both sides of the fixed tooling in a node form the stress relieving extends throughout the entire length of the elongate member.

The machine for accomplishing this process as described herein is a spindle and/or coordinated plural spindles in which the spindle is rotated and the spindle is selectively displaced in eccentricity simultaneous with the rotation. By means of a crank arm which is an extension of the rotating eccentric the elongate stock is gripped and orbital rotation of increasing magnitude is imparted to the elongate stock, while the stock is held in a true center position in spaced relation from the crank arm. The deflection of the elongate stock is increased progressively until the deflection exceeds the yield point of the material of the stock. The increase is the consequence of increasing the amount of eccentric movement in the spindle while it is continually rotated. Then the eccentricity is gradually and regressively reduced to zero in the moving spindle and accordingly the elongate stock is centered and the crank ari'n ceases its motion while the spindle continues to rotate. ,At the center position and zero deflection the crank locates the elongate stock between at least two fixed tooling positions and on the axis passing through the two fixed points. in the case of a desired offset in the elongate member the zero position of the moving tooling may be offset by the precise desired final position of the stock. The stock, where possible by its cross section configuration, can be axially displaced by a new piece of stock to be straightened or the tooling and crank arm may be gated to discharge the straightened element and to receive a new element, here .the elongate stock is irregular, for example, in its cross section configuration. The motion desired is best achieved by pairing the eccentric spindles and when so paired plural socketing of the crank arm plate and plural tooling will allow a plurality of elongate stock pieces to be straightened at once. Such paired units are then limited in number of units simultaneously treated only by the power available from the spindles. The spindles may be used in face to face pairing and with synchronized movement to either add power or add a simultaneous movement to a piece of elongate stock coordinated with the facing spindles. in such instances, for example, a plurality of eccentric oscillations at diverse points can be synchronously imparted to the same or different pieces of stock.

Accordingly, the machine comprises a mechanism for imparting rotation to at least one and preferably two spindles; a mechanism for selectively imparting gradual progressive and regressive eccentricity to the output of the spindle while not interfering with rotation of the spindles; a crank arm element transmitting the motion generated by the spindles to a piece of stock and including gripping means for the stock; ways on which fixed tooling is located; and a machine frame which may include transfer equipment designed to accomodate parts treated in the machine.

The'mechanism for imparting an eccentric motion during rotation comprises a vane type hydraulic motor which rotates with the driven spindle and is keyed to selectively rotate or position a central shaft axially and eccentrically positioned in the spindle. Both the rotation of the spindle and the movement of the eccentric imparting shaft are coordinated in a flanking parallel spindle in counter rotation to the first spindle. In this manner a single drive operates the two spindles and a single hydraulic drive operates the vane driven eccentric mechanism in both spindles. The crank arm then becomes a crank plate in which any point thereon generates a circular orbiting motion exactly corresponding to the amount of eccentricity imparted by the spindles. The crank plate does not rotate, but oscillates in its plane transverse of the work axis.

it will be appreciated that in some instances where for example the shaft form includes two or more ultimate parallel and offset axes as in crank shafts, the fixed tooling may utilize offset centers from the zero deflection point of the oscillating tooling member and the desired offset is ultimately imparted in reproducible fashion after progressive and regressive displacement of the stock and return to the zero point, where the maximum selected displacement by the moving tooling exceeds the yield point of the material of the stock.

Since the axes of the stock are bowed by the incremental oscillating displacement, relative displacement occurs on each side of the fixed tooling, the centers being retained by virtue of the spherical seats of the fixed tooling. Accordingly, the process and apparatus is adaptable to outboard movable tooling where the displacement is imparted out-board of the two or more fixed tooling points and the displacement then occurs between the fixed tooling points in node form.

SPECIFIC DESCRIPTION Referring to the drawings, and with particular reference to the FIG. 1, a machine 11 in accord with the present invention is shown.. The machine 11 includes a base or frame 12 which supports the spindle drive head 13, a motor 14 providing rotation to the spindles within the drive head 13 through the power transmission element 15 over the sheave 16 and powering the spindles. A vane type hydraulic motor 17 is operably secured to the spindledrive head 13 and rotates with the spindles therein for imparting selected eccentric motion to the output of the spindles. A motion translating element 18 provides monitoring means reflecting the amount of eccentric mechanically imparted to the spindles by the vane motor 17. This provides a convenient calibrating means for automation of the machine and process. As will be appreciated the motion translating element 18 could, where desired, impart selected eccentricity in lieu of the vane motor 17 by use of a lineal actuator such as a power cylinder (not shown) for example. T-slotted machine ways 19 are positioned on the drive heads 13 and on the outboard tooling support or pedestal 20 as best seen in FIG. 2. The hydraulic pump located within the tank 21 is driven by the motor 22 and the hydraulic line 23 is swivel connected at the swivel 24 to the vane motor 17. Collaterally, the hydraulic power available from the hydraulic drive power package 25 is piped or manifolded to the overhead transfer mechanism 26 and transfer racks 27 as by appropriate power cylinders or motors 28 lineally' acting on the transfer bar 29 to insert workpiece 30 into the fixed tooling elements 31 and into the oscillating or mo able tooling piece 32 which is eccentrically driven by connection to the spindle extension 33. In the transfer structure 26, as shown, completed workpieces are axially shifted by the new workpieces to disengagement from the tooling 31 and 32 and the workpieces are deposited on the transfer rack 27 for subsequent delivery, inspection and/or packaging. Motors or cylinders, not shown, actuatethe transfer rack 27 in a well known manner to remove the stock 30 after treatment. The transverse transfer way 34 treating stock discharge is best seen in FIG. 1. The hydraulic power package 25 may be located elsewhere than as indicated-in the FIG. 2, but its integral connection with the machine frame 12 makes unitary the entire machine 11.

Where, for example, the unusual cross section of workpieces 30 will not admit axial loading as indicated in FIGS. 1 and 2 the machine superstructure 35 may be removed and by gating the tooling 31 and 32 the loading of workpieces 30 can be accomplished from the side or top of the machine as viewed in FIGS. 1 and 2. Controls, as may be desired for sequencing may be hydraulic, electrical or pneumatic, or a combination of these and control panels may be conveniently attached to the structure and selectivity of the magnitude of oscillations and sequence monitoring is possible through the translating element 18.

Operationally, stock 30 is inserted in the tooling 31 and 32 with the spindle extensions 33 rotating at zero deflection or zero eccentricity so that no motion occurs in the oscillating pitman or crank arm 36 and the oscillating tool piece 32 is accordingly stationary. When the work piece 30 is thus positioned the vane motor 17 is energized and in its rotation with the spindle imparts an eccentric shift to output of the spindle extensions 33. Hence, the pitman 36 is progressively displaced and oscillated under the influence of rotation and eccentricity and the movable tooling 32 is caused to oscillate progressively at increasing amplitude. This displaces the stock 30 except as spaced apart centers are maintained by the fixed tooling 31. As will be seen the tooling 31 is spherically seated so that as axial deflection in the stock 30 occurs the center established by the tooling 31 remains the same. Displacement then proceeds under the influence of vane motor 17 until the yield point of the material comprising the workpiece 30 is exceeded. Thereupon the vane motor 17 reverses and regressively diminishes the eccentricity in the spindles to a zero value while the spindles are rotating. The stress relieved stock 30 can then be removed, without the necessity of stopping the rotation of the spindles and a subsequent workpiece 30 is positioned for straightening. As previously indicated, the transfer structure 26 can be modified in accord with specific problems in specific workpieces 30 but as described the transfer system 26 allows axial loading and discharge at relatively high production speeds. The arrangement, utilizing the eccentric power of the van motor 17, while under constant rotation by motor 14, minimizes overall power requirements as contrasted with press type apparatus and separate drive elements, both acting in separate transverse planes. As will be appreciated by those skilled in the art the machine 11 is substantially simplified and compacted.

In FIG. 3 the spindle drive head 13 is best understood from an external point of view as comprising a case 40 in which drive spindles 41 are axially journalled in parallel spaced apart registry and to the end of which the vane motor 17 is axially secured. The hydraulic swivel 24 is axially connected to the vane motor 17 so as to allow the case of the vane motor 17 to rotate with the spindles 41. The spindles 41 are rotated by means of a worm (as will be seen) and gearing through the worm shaft 42 extending from the spindle case 40. This is best understood by reference to FIG. 4. In FIG. 4 the spindle drive head 13 is seen to journal a pair of rotatable spindles 41, the output stubs 33 of which were seen in reference to FIG. 2. The spindles41 actually comprise a tubular outer element 45 and each having an eccentric bore 46 longitudinally therethrough. A shaft element 47 is positioned in each of the bores 46 and these assemblies are journalled in adjacent parallel relation in the case 40 journalled by the antifriction bearing elements 48 and 49. A worm gear 50 is driveably secured to one of the tubular elements 45 and meshed with the worm 51 turned by the worm shaft 42 (see FIG. 5). The gears 52 are also driveably secured to the tubular elements 45 and are in registering mesh with each other. Accordingly, rotation of one tubular member 45 causes equal and opposite rotation of the other members 45 on the axis established by its bearings 48 and 49. Also driveably secured to one of the tubular elements 45 at one end thereof is the case 53 of vane motor 17 and accordingly the case 53 of vane motor 17 rotates with the tubular element 45. The vane motor 17 generally parallels the structure set forth in the US. Patent No. 2,827,943 and the vane rotates through an arc of 120 against internal stops. The vane shaft 55 rotates with the vane (not shown) and is coupled to one of the shafts 47 by a coupler 56 cross keyed on one side to the vane shaft 55 and on the other side to the end of shaft 47. In this manner the shaft 47 is selectively rotatable during rotation of the entire spindle 41 and the angular change imparted to the shaft 47 determines the amount of eccentricity imparted to the output stubs 33 of the spindles 41 from a zero value to a maximum value dependent upon the eccentricity of bore 46. While the vane motor 17 acts on only one shaft 47 directly, mechanical synchronization of both shafts 47 is achieved by the mimicking linkage 57 to exactly coordinate the eccentricity in both shafts 47. A pair of gear elements 58 are positioned in free rotation on the tubular elements 45 in meshed register. A boss ring 59 secured to the gear element 58 provides an axial extension therefrom and through which pins 60 radially extend. The stub pins 60 are radially secured in the shafts 45 in an opposite directional relation from centricity of the output stubs 33 by separate and coordinated rotation.

The motion translating element 18 comprises a cylindrical cage 70 secured to one of the tubular spindle elements 45 and hence rotatable therewith. A spiral cam groove 71 is radially and spirally defined through the wall of the cylindrical cage 70. This provides a guide cam groove 71 for. a roller ended pin 72 which radially extends from a piston element 73 which extends from an axial bore in one of the shafts 47 and is keyed for rotation therewith by the slot 74 in a shaft extension 75. Hence, as relative rotation of the shaft 47 occurs during continual rotation of the tubular elements 45, the relative difference in rotation and hence the degree of eccentricity is translated into lineal in and out motion of the piston 73 and thereby provides a monitoring means for selective control over the eccentricity desired in any given job. This is conveniently read out as by limit switches 76 and 77 variably set to provide a limiting control over the process and sequencing control for overall control elements not a part of the present invention. A pressure relief passage 78 is provided to avoid air entrapment back of the piston 73. While functioning as a monitor and limiting means for extremes of eccentricity the element 18 could accomodate a power actuator (lineal) to accomplish the motion achieved by the vane motor 17.

The FIG. best illustrates the simultaneous rotation of the spindles 41 through the worm 51 acting on the worm gear 50 which causes meshed gears 52 to rotate the spindles 41 and additionally indicates the ways of T-slotted tooling plates 19 secured to the top of the spindle case 13. The T-slots 80, as will be seen provide variable position fixed mounts for tooling elements.

. In the section view of FIG. 6 the motion translating element 18 is shown and the cross slot in one of the shafts 47 for connection to the vane motor 17 (FIG. 4) is best understood. In addition, fixed tooling elements 31 are seen secured to the tooling plate 19 and in phantom line additional fixed tooling 31 is indicated where the load capacity of the spindle head 13 will admit ad ditional productivity.

In FIGS. 7, 8 and 9 the pitman or crank arm plate 90 is shown secured to the spindle extensions 33 and extending upward to embrace the movable tooling elements 32. Since the spindles 41 are constantly rotating it will be observed that stubs 33 are joumalled in the crank arm plate 90 as by the anti-friction bearing 91 so that motion is only imparted to the pitman or crank arm plate 90 when an eccentric relation is impressed on the drive spindles 41. When an eccentric relation is established in the spindles 41 the crank arm plate 90 does not rotate but rather oscillates to impart a coordinated movement to both of the movable tooling fixtures 32. The amplitude of the oscillations are exactly corresponding to the degree of eccentricity and since rotation is continuing in the spindles 41 any point taken in the crank arm 36 describes an orbital trace about a zero starting point coinciding with a zero eccentricity.

With reference to FIG. 7, the phantom line extension of the crank arm plate indicates how additional moving tooling elements can be attached where the capacity of the spindle heads 13 permit. The replaceable moving tool block 92 defines an orifice 93 therethrough having a cross section and clearance corresponding to the cross section of the workpiece 30 at the point or in the plane of displacement. A bevel relief is axially provided to accomodate the bowing of elongate members during displacement and to facilitate insertion of stock 30. About one of the spindles 33 a cage track 94 is provided allowing lineal movement of the bearing 91 in respect to one of the spindle extensions 33. This assures the coordination of eccentric rotating motion in the spindle extensions 33. This is secured in place by cover 95 attached to the crank arm plate 90.

In FIGS. 10, 11 and 12 the fixed tooling elements 31 are shown. These comprise a mounting carriage 100, which by means of bolts 101 are selectively secured to the tooling ways 19 in the T-slots 80, thereof (see FIG. 5). The tooling block 102 defines an orifice 103 through which the workpiece 30 extends (see FIG. 2). As in the instance of the movable tooling 32, the orifice 103 includes a relief bevel 11 1 flaring outward at each end to accommodate flexure in the elongate member or workpiece 30 This also allows for ease of axial loading as seen in FIG. 2 since the workpiece 30 can then guide itself through the orifice 103. In addition the block 102 is surrounded by a spherical cage 104 limitedly movable universally in a mating spherical seat element 105 provided in the tooling carriage or frame 100. This joumalling is complemented by a swivel slide element 106 which allows controlled limited float of the fixture 31 in all axes so long as the center point 112 remains fixed. The swivel slide 106 comprises a trunnion block 107 having an axle 108 and bearings'109 as between cheek plates 110 between which the tooling block 102 is secured. As previously indicated additional fixed tooling elements 31 may be added flanking the tooling shown in the carriage 100. It will also be appreciated that the orifices 103 accommodating the workpieces 30 may be variously configured to accommodate varying cross sections of stock and, the fixed center tooling 31 may be gated for side loading where the part cannot be axially loaded.

FIG. 13 schematically illustrates two spindle drive heads 13 in juxtaposed face-to-face relation and synchronized to apply additional drive power where desired or where necessary in peculiar stress relieving or straightening operations. In this FIG. 13 the node form of displacement of workpiece 30 between fixed tooling elements is observed in phantom line.

FIG. 14 schematically expresses the mechanism and process. The rotating and variably eccentric drive element 200 transmits a progressive oscillation of increasing amplitude to the workpiece 201 by means of a pitman 202, the work 201 being supported between fixed tooling abutments 203 in spaced apart relation. The pitman 202 includes tooling 204 movable therewith and surrounding the workpiece 201 intermediate the fixed tooling 203, although as will be appreciated, the node form of displacement can be obtained between the fixed tooling 203 by an outboard connection of pitman 202 to stock 201. As the drive 200 is rotating the degree of eccentricity is increased to a point beyond where the displacement exceeds the yield point of the material comprising the workpiece 201. This is reflected in increasing deflection of the work piece 201 as represented by the axial lines in phantom in the FIG. 14. Thereafter, the eccentricity is reduced and returned to the zero starting point as determined in the drive 200. At this point oscillations stop and the workpiece 201 is thoroughly stress relieved. As described elsewhere plural workpieces can be handled simultaneously by multiple tooling. In FIG. the oscillating motion is exemplified where the pitman 202 in response to eccentricity in the drive 200 moves the workpiece orbitally about a starting point as shown to a displacement beyond the yield point to phantom positions 201' while all of the time oscillating and then the stock 201 is returned to the zero deflection position. All points on the tooling pitman 202 oscillate equally in all directions in the plane of the pitman 202 at an amplitude established by the degree of eccentricity variably applied to the drive 200.

In FIG. 16 a schematic cross section of an elongate member 300 is shown and taken at the plane in which displacement force is incrementally applied. The center 301 of the elongate member 300 is chucked at zero deflection in the movable tooling fixture. At zero deflection the spindles 41 are rotating at a working speed by the movable tooling 32 is stationary so that chucking is possible conforming the workpiece to the zero condition in the movable fixture. Then, by progressive and gradual movement of the vane motor 17 the output of the spindle is made eccentric and the amount of eccentricity with continuing rotation imparts an oscillation about the zero center. The progress of the center 301 is indicated by the solid line trace as eccentricity is proceeding. Each point in the line may include several oscillations about the center 301 depending upon the rotational speed of the spindles. Then after the deflection or displacement has exceeded the limit of the yield point (displacement A) of the material comprising the elongate element 300 and with continuing rotation of the spindles 41, the eccentricity is gradually reduced and the spiral trace in phantom line indicates the regressive return to center 301 of the workpiece at final zero deflection.

Because of the continuing rotation of the spindle causing oscillation about the center 301 the schematic trace of FIG. 16 can only suggest the gradual and continuing orbital action from zero eccentricity to select maximum eccentricity and return to zero, and where the zero point coincides with the desired end final location for straightening.

The process and apparatus introduce new concepts in straightening since as between fixed tooling the amplitude of oscillations are repeated in a node form so that substantially an entire elongated object is equally stressed with the fixed tooling establishing zero points as well as the ultimate position of the oscillation imparting tooling. The significance of this, where the movement of the stock exceeds its yield point, is that plural axis straightening is possible as for example in crank shafts as has been described, one axis, for example, being established by fixed tooling. The more usual situation in regular shafting rods, tubes and the like is where the fixed centers and the moving centers are brought into. axial register. As will be appreciated, on loading in the usual situation, the part served, commences by being conformed to its final position and is then stress relieved and returned to its end final position.

In unusual instances, as for example in tubular extensions from difl'erential housings the oscillations may be imparted at the end of the tubular extensions while holding rigidly at the housing on a true center point. Where tubular stock is oscillated the crank arm may be inserted in the end of the stock.

Controls for automating and sequencing comprise no part of the present invention except as the eccentric movement is reflected in lineal read out to provide a process and apparatus control monitor of eccentricity and consequent oscillation deflection.

The apparatus produces a quality straightened and stress relieved product without manual checking and at reproducible accuracy.

Having thus described our process and an embodiment of an apparatus practicing the process, others skilled in the art will percieve improvements, modifications and refinements and such improvements, modifications and refinements are intended to be included herein limited only by the scope of our hereinafter appended claims.

We claim:

I. In a method for straightening elongate elements such as shafts, tubing, bars or the like by supporting an elongate member by at least two spaced apart points, said points being fixed and establishing therethrough a straight line and simultaneously movably gripping said elongate element at a selected point intermediate said fixed points;

moving said intermediate gripping element in an oscillating path while rotating to define a progressively and outwardly spiralling oscillating path about the axis established by said fixed points, thereby dynamically deflecting said elongate element beyond the yield point of the material comprising said elongate element and through at least one revolution in the maximum deflected position and then regressively diminishing the deflection and oscillation to a zero point on the axis established by said fixed points, the improved steps of loading said elongate elements axially through open ends of said fixed spaced points and said intermediate gripping element and axially unloading said elongate elements by insertion of the next following elongate element.

2. In the process of claim 1 wherein adjacent sets of open ended fixed points are provided and a single intermediate gripping element is simultaneously aligned with said fixed points and a plurality of said elongate elements are thrust therethrough whereby said plural elongate elements are axially loaded and unloaded for simultaneous parallel insertion straightening and removal.

3. In the process of straightening elongate elements as set out in claim 1 extended to achieve progressive spiral deflection at plural points in the same elongate element, the steps of placing an elongate element axially through a plurality of fixed points and through a plurality of intermediate aligned gripping elements productivity includes plural adjacent axial sets of fixed points simultaneously acted upon by commonly moved gripping elements and each of said elongate elements movable in an axial path through said fixed points and said gripping element, the next adjacent of said elongate elements axially displacing the ones ahead of them in loading and unloading.

t i It t 

1. In a method for straightening elongate elements such as shafts, tubing, bars or the like by supporting an elongate member by at least two spaced apart points, said points being fixed and establishing therethrough a straight line and simultaneously movably gripping said elongate element at a selected point intermediate said fixed points; moving said intermediate gripping element in an oscillating path while rotating to define a progressively and outwardly spiralling oscillating path about the axis established by said fixed points, thereby dynamically deflecting said elongate element beyond the yield point of the material comprising said elongate element and through at least one revolution in the maximum deflected position and then regressively diminishing the deflection and oscillation to a zero point on the axis established by said fixed points, the improved steps of loading said elongate elements axially through open ends of said fixed spaced points and said intermediate gripping element and axially unloading said elongate elements by insertion of the next following elongate element.
 1. In a method for straightening elongate elements such as shafts, tubing, bars or the like by supporting an elongate member by at least two spaced apart points, said points being fixed and establishing therethrough a straight line and simultaneously movably gripping said elongate element at a selected point intermediate said fixed points; moving said intermediate gripping element in an oscillating path while rotating to define a progressively and outwardly spiralling oscillating path about the axis established by said fixed points, thereby dynamically deflecting said elongate element beyond the yield point of the material comprising said elongate element and through at least one revolution in the maximum deflected position and then regressively diminishing the deflection and oscillation to a zero point on the axis established by said fixed points, the improved steps of loading said elongate elements axially through open ends of said fixed spaced points and said intermediate gripping element and axially unloading said elongate elements by insertion of the next following elongate element.
 2. In the process of claim 1 wherein adjacent sets of open ended fixed points are provided and a single intermediate gripping element is simultaneously aligned with said fixed points and a plurality of said elongate elements are thrust therethrough whereby said plural elongate elements are axially loaded and unloaded for simultaneous parAllel insertion straightening and removal.
 3. In the process of straightening elongate elements as set out in claim 1 extended to achieve progressive spiral deflection at plural points in the same elongate element, the steps of placing an elongate element axially through a plurality of fixed points and through a plurality of intermediate aligned gripping elements located between each two successive fixed points and simultaneously oscillating and rotating the plurality of intermediate gripping elements, whereby straightening is achieved in plural zones of the same elongate element.
 4. In the claim 3 the additional step of axially loading and unloading elongate elements, the next adjacent element axially displacing the one before it in each cycle. 